DE112020004569B4 - Hydraulic torque converter - Google Patents

Abstract

Hydraulic torque converter, comprising:
a housing (2) arranged around a rotational axis (X) for receiving an input torque;
a pump impeller (3) arranged around the axis of rotation (x) and comprising a pump impeller housing (31), a pump impeller core ring (32) and a plurality of pump impeller blades (34);
a turbine (4) arranged around the axis of rotation (X) and axially opposite the pump impeller (3) and comprising a turbine housing (41) and a plurality of turbine blades (43);
an output hub (6) arranged around the axis of rotation (X) and fixedly connected to the turbine housing (41) for outputting a torque;
wherein the hydraulic torque converter further comprises an inner friction disc (5) arranged around the axis of rotation (X) and axially positioned between the pump impeller (3) and the turbine (4), wherein a plurality of elastic components (7) are arranged on the inner friction disc (5) and are held between the inner friction disc (5) and the pump impeller core ring (32) to transmit the torque from the pump impeller (3) to the inner friction disc (5) via the plurality of elastic components (7); and
wherein the turbine (4) is displaceable between a locked position, in which the turbine housing (41) engages the inner friction disc (5) and forms a locking connection with it, and a released position, in which the turbine housing (41) disengages from the inner friction disc (5).

Description

Technical field

The present disclosure relates to a hydraulic torque converter and more precisely to a hydraulic torque converter with an internal friction disc.

background

A hydraulic torque converter is typically installed between the engine and the transmission of a motor vehicle with an automatic transmission. The hydraulic torque converter is used to transfer the engine's power to the transmission using a fluid (usually oil), thereby transmitting and modifying the torque.

The hydraulic torque converter typically comprises a housing, a pump impeller, a turbine, a lock-up clutch, a shock absorber, and an output hub. The pump impeller and the turbine are axially opposed to each other. The pump impeller has an impeller housing that rotates integrally with the housing and a plurality of impeller blades attached to the impeller housing. The turbine has a turbine housing that is fixedly connected to the output hub and a plurality of turbine blades attached to a side of the turbine housing facing the pump impeller. The turbine housing and the pump impeller housing together enclose and define a recirculation circuit, as is known in the prior art.

In some cases of the prior art, the bridging coupling is configured between the pump impeller and the turbine. In the Chinese patent application CN 106 574 701 A For example, the turbine housing serves as a piston disc of the bypass clutch and has a first friction segment that is axially movable in order to engage with or disengage from the pump impeller housing, which has a second friction segment. In the US patent application US 2015/0152951A1 A first piston disk and a second piston disk are arranged between the pump impeller housing and the turbine housing, wherein the first piston disk is suspended between the turbine and the second piston disk, while the second piston disk is connected to the turbine without restricting its axial displacement.

In each of the aforementioned prior art designs, the shock absorber is located outside the circulation loop, which is jointly defined by the turbine housing and the pump impeller housing. The shock absorber typically comprises a driving disc connected to the lock-up clutch and a driven disc fixed to the output hub, as well as a circumferentially acting elastic component. The circumferentially acting elastic component is positioned between the driving and driven discs. It has been observed that the presence of multiple shock absorber components occupies a significant amount of space within the torque converter, particularly in the axial direction.

From the DE 196 26 685 A1 and the JP S55 - 76 254 A Incidentally, different bridge clutch and damper arrangement variants are known in a torque converter with a damper in the pump impeller and turbine chamber.

Overview of the invention

Therefore, one of the objectives of the present disclosure is to improve the utilization rate of the interior space of the hydraulic torque converter and to simplify the overall size of the hydraulic torque converter by means of a sophisticated design of a component with a dual function.

The problem is solved by a hydraulic torque converter with the features of claim 1. Advantageous further developments are found in the dependent claims.

The present disclosure provides a hydraulic torque converter comprising: a housing arranged around an axis of rotation for receiving an input torque; a pump impeller arranged around the axis of rotation and comprising a pump impeller housing, a pump impeller core ring, and a plurality of pump impeller blades; a turbine arranged axially relative to the pump impeller around the axis of rotation and comprising a turbine housing and a plurality of turbine blades; an output hub arranged around the axis of rotation and fixedly connected to the turbine housing for outputting a torque; wherein the torque converter further comprises an inner friction disk arranged around the axis of rotation and axially between the pump impeller and the turbine, on which a plurality of elastic components are arranged, wherein the A multitude of elastic components are held between the inner friction disc and the pump impeller core ring to transmit a torque from the pump impeller to the inner friction disc via the multitude of elastic components; and wherein the turbine is displaceable between a locked position in which the turbine housing engages the inner friction disc and forms a locking or detent connection, and a released position in which the turbine housing disengages from the inner friction disc.

In the hydraulic torque converter according to the present disclosure, the inner friction disc serves as a component of both the lock-up clutch and the shock absorber, and simultaneously acts as a retaining disc for the elastic components of the shock absorber and as the friction disc of the lock-up clutch. Two components that are usually separate are combined into one, and a shock absorber, which is usually located outside a first chamber formed by the pump impeller housing and the turbine housing, is arranged within the first chamber. Therefore, the torque converter can have a smaller volume, and the space saved provides ample design options, such as for adding additional components, etc. Furthermore, the torque converter can be lighter, which makes it possible to reduce the energy consumption of motor vehicles equipped with the torque converter, thus meeting current environmental protection requirements for energy saving and emission reduction.

In some embodiments, the inner friction disc has an annular shape with an inner circumferential section located on its radially inner side. This inner circumferential section has a plurality of windows extending circumferentially for holding an elastic component. Two adjacent windows for holding an elastic component are separated circumferentially by a radial partition, and the plurality of elastic components are held axially between the plurality of windows for holding an elastic component and the pump impeller core ring.

Consequently, the shock absorber components (the pump impeller core ring, the elastic components, and the windows for holding an elastic component) are located in a central position in the radial direction of the first chamber, without obstructing the transmission path of the hydraulically driven fluid between the pump impeller and the turbine. Therefore, according to the present disclosure, the hydraulic torque converter fully utilizes the interior space at the radial central position of the first chamber to accommodate the shock absorber, significantly reducing the size of the hydraulic torque converter in the radial direction and resulting in a compact structure that aligns with the current trend toward component size reduction in the automotive industry.

In some embodiments, the pump impeller core ring has a plurality of drive strips extending towards the inner friction disc. Each elastic component is compressed circumferentially between the drive strip of the pump impeller core ring and the radial partition of the inner friction disc.

In some embodiments, the inner friction disc has an outer circumferential section that is radially outside the inner friction disc and has a first surface facing the pump impeller and a second surface facing the turbine, and a friction plate is arranged on the second surface to form a snap-fit connection with the turbine housing.

In some embodiments, a first locking or stop bushing with an annular shape around the axis of rotation is provided on the first surface of the outer circumferential section of the inner friction disc for axially supporting the inner friction disc when the turbine is in the locked position.

In some embodiments, a sealing ring is provided on the first surface of the outer circumferential section of the inner friction disc.

In some embodiments, the inner friction disc is provided with a plurality of centering projections for centering the sealing ring and/or the first stop bushing relative to the axis of rotation. The sealing ring has an annular shape around the axis of rotation and is used to form a fluid seal between the pump impeller housing and the inner friction disc when the turbine is in the locked position, thereby ensuring the pressure differential between the first chamber and a second chamber. Therefore, the inner friction disc and the turbine housing form a tight and secure frictional connection, consequently ensuring the efficiency of torque transmission in rigid transmission mode.

In some embodiments, the outer and inner circumferential sections of the inner friction disc are connected by a plurality of radial webs, with a circumferentially extending fluid flow window formed between adjacent radial webs. The fluid flow window allows the hydraulic transmission fluid circulating in the first chamber to flow through it, while simultaneously reducing the weight of the inner friction disc and the entire torque converter.

In some embodiments, each radial web and the corresponding radial partition of the inner circumferential section are aligned with each other in the radial direction, thereby improving the mechanical strength of the inner friction disc as a torque transmission component.

In some embodiments, a second stop bushing with an annular shape around the axis of rotation is arranged between the output hub and the housing for axially supporting the output hub when the turbine is in the released position.

In some embodiments, the second stop bushing is provided with a plurality of radially extending fluid passages to allow the fluid to flow into or out of the space between the turbine housing and the casing.

The present disclosure also provides a motor vehicle having the hydraulic torque converter described above.

Brief description of the drawings

• 1 eine schematische Darstellung eines hydraulischen Drehmomentwandlers nach einer beispielhaften Ausführungsform der vorliegenden Offenbarung ist;
• 2 eine auseinandergezogene Ansicht eines hydraulischen Drehmomentwandlers nach einer beispielhaften Ausführungsform der vorliegenden Offenbarung ist;
• 3 eine innere Reibscheibe eines hydraulischen Drehmomentwandlers nach einer beispielhaften Ausführungsform der vorliegenden Offenbarung zeigt;
• 4 die Strukturen der äußeren und inneren Umfangsabschnitte der inneren Reibscheibe des hydraulischen Drehmomentwandlers nach einer beispielhaften Ausführungsform der vorliegenden Offenbarung zeigt;
• 5 einen Pumpenlaufrad-Kernring eines hydraulischen Drehmomentwandlers nach einer beispielhaften Ausführungsform der vorliegenden Offenbarung zeigt;
• 6 eine zweite Anschlagbuchse eines hydraulischen Drehmomentwandlers nach einer beispielhaften Ausführungsform der vorliegenden Offenbarung zeigt;
• 7 ausführlich einen Teil der inneren Reibscheibe eines hydraulischen Drehmomentwandlers nach einer beispielhaften Ausführungsform der vorliegenden Offenbarung veranschaulicht;
• 8 einen Fluidströmungsweg eines hydraulischen Drehmomentwandlers in einem arretierten Zustand nach einer beispielhaften Ausführungsform der vorliegenden Offenbarung zeigt; und
• 9 einen Drehmomentübertragungsweg eines hydraulischen Drehmomentwandlers in einem arretierten Zustand nach einer beispielhaften Ausführungsform der vorliegenden Offenbarung zeigt.

The accompanying drawings are incorporated into the description and form part thereof. Together with the preceding general description and the detailed description of exemplary embodiments and methods listed below, the drawings serve to illustrate the principles of this disclosure. The objectives and advantages of this disclosure will become apparent upon studying the following description in accordance with the accompanying drawings, in which identical elements the same or similar reference numbers are given and in which:

• 1 a schematic representation of a hydraulic torque converter according to an exemplary embodiment of the present disclosure;
• 2 an expanded view of a hydraulic torque converter according to an exemplary embodiment of the present disclosure;
• 3 an inner friction disc of a hydraulic torque converter according to an exemplary embodiment of the present disclosure;
• 4 the structures of the outer and inner circumferential sections of the inner friction disc of the hydraulic torque converter according to an exemplary embodiment of the present disclosure;
• 5 a pump impeller core ring of a hydraulic torque converter according to an exemplary embodiment of the present disclosure;
• 6 a second stop bushing of a hydraulic torque converter according to an exemplary embodiment of the present disclosure;
• 7 a detailed illustration of a part of the inner friction disc of a hydraulic torque converter according to an exemplary embodiment of the present disclosure;
• 8 a fluid flow path of a hydraulic torque converter in a locked state according to an exemplary embodiment of the present disclosure; and
• 9 shows a torque transmission path of a hydraulic torque converter in a locked state according to an exemplary embodiment of the present disclosure.

Detailed description of the embodiments

Reference will now be made in detail to the exemplary embodiments and methods of the present disclosure, which are illustrated in the accompanying drawings, where identical reference numbers denote the same or corresponding components. It should be noted, however, that the present disclosure, in its broader aspects, is not limited to specific details, representative devices and methods, and illustrative examples shown and described in connection with the exemplary embodiments and methods.

This description of exemplary embodiments should be read in conjunction with the accompanying drawings, which are considered part of the overall written description. In the description, relative terms such as "up" or "upwards,""down" or "downwards,""left,""right," and derivatives thereof (e.g., "downwards,""upwards," etc.) should be interpreted as referring to the orientation described or shown in said drawings. These relative terms are used for the sake of clarity and are not intended to prescribe a specific orientation. Unless expressly stated otherwise, the terms "connected,""coupled," and the like refer to the relationship in which structures are directly or indirectly attached or affixed to one another by means of intervening structures, as well as the movable or fixed attachment or the movable or fixed relationship. The term "operationally connected" is a connection relationship that enables associated structures to exhibit the connection relationship during operation or actual use. Furthermore, the words "one" and "the" used in the claims refer to at least one, and the word "two" used in the claims refers to at least two.

A first exemplary embodiment of a hydraulic torque converter 1 is generally in 1 The hydraulic torque converter 1 receives an input torque from a power machine and transmits the torque to an input shaft (not shown) of a gearbox in, for example, a motor vehicle.

It should be clear that the axial and radial orientations are considered in relation to the axis of rotation X of the hydraulic torque converter 1. Relative expressions, such as "axial", "radial", and "circular", are, respectively, relative to their orientations parallel to the axis of rotation X, perpendicular to the axis of rotation X, and circular around the axis of rotation X.

The drawings discussed here show only one half of the hydraulic torque converter 1, that is, the cross-section of the section or partial part above the axis of rotation X of the hydraulic torque converter 1. As is known in the prior art, the hydraulic torque converter 1 is circumferentially symmetrical about the axis of rotation X.

The hydraulic torque converter 1 has a housing 2 arranged around a rotational axis X as an input element. The housing 2 receives a torque from the power machine as the input torque of the hydraulic torque converter 1. The housing 2 rotates at the same speed as an output shaft of the power machine.

The hydraulic torque converter 1 also has an output hub 6 as an output element, which is arranged around the axis of rotation X. The output hub 6 is coupled to and coaxially arranged with an input shaft of the gearbox. For example, the output hub 6 can be provided with internal splines for non-rotatable coupling of the output hub 6 to the input shaft of the gearbox, which is provided with complementary external splines. Alternatively, a weld or other connection can be used to fix the output hub 6 to the input shaft of the gearbox.

The hydraulic torque converter 1, which is in 1 The figure shown has a pump impeller 3 arranged around the axis of rotation X, a turbine 4 arranged around the axis of rotation X and aligned coaxially with the pump impeller 3, and a guide vane arranged between the pump impeller 3 and the turbine 4.

The pump impeller 3 comprises a substantially annular pump impeller housing 31, a pump impeller core ring 32, and a plurality of pump impeller blades 34, which are fixedly attached to the pump impeller housing 31 and the pump impeller core ring 32, for example by brazing. The pump impeller 3 is mounted to the housing 2 and consequently connected to a drive shaft of the power machine (or flywheel) to rotate at the same speed as the output shaft of the power machine. In some embodiments, the impeller housing 31 is located, as in 1 shown, axially opposite the housing 2 and is attached to the housing 2 by a weld section 21.

The turbine 4 is arranged axially opposite the pump impeller 3 and can be hydraulically driven by the latter. The turbine 4 comprises a turbine housing 41 and a plurality of turbine blades 43. The turbine 4 includes a turbine housing 41, a substantially annular turbine core ring, and a plurality of turbine blades 43, which are rigidly attached to the turbine housing 41 and the turbine core ring, for example, by brazing. The turbine housing 41 is rigidly connected to the output hub 6, for example, by rivets. The turbine blades 43 are attached to a side of the turbine housing 41 facing the pump impeller 3. The turbine and the guide vane together form a recirculating circuit. In the hydraulic transmission mode of the hydraulic torque converter 1, the pump impeller 3 and the turbine 4 can transmit power through a fluid without a rigid connection, as is known in the prior art.

The pump impeller housing 31 and the turbine housing 41 define a first chamber 11 (or a recirculation chamber) between them. The turbine housing 41 and the housing 2 define a second chamber 12 between them. With respect to 1 The first chamber 11 is located on the left side of the turbine housing 41 and the second chamber 12 is located on the right side of the turbine housing 41.

According to some embodiments of the present disclosure, the hydraulic torque converter 1 further comprises a substantially annular inner friction disc 5, which is arranged around the axis of rotation X and is axially positioned between the pump impeller 3 and the turbine 4.

The inner friction disc 5 is designed as part of the lock-up clutch of the hydraulic torque converter 1. The lock-up clutch is configured to mechanically transmit torque when it is in the locked position. The lock-up clutch is generally locked after the actuation process of the vehicle's hydraulic transmission to prevent efficiency loss caused, for example, by a sliding event between the turbine 4 and the pump impeller 3. The lock-up clutch also includes the turbine housing 41, which forms a piston section of the lock-up clutch. Consequently, the turbine housing 41 can be axially displaced between the locked and unlocked positions. In the locked position, the turbine housing 41 engages and forms a latching connection with the inner friction disc 5, with the hydraulic torque converter 1 operating in rigid transmission mode. In the unlocked position, the turbine housing 41 is released from the inner friction disc 5, and the hydraulic torque converter 1 operates in hydraulic transmission mode.

The inner friction disc 5 also forms part of a shock absorber of the hydraulic torque converter 1. Regarding the 2 and 4 The inner friction disc 5 is provided with a plurality of elastic components 7, which are held between the inner friction disc 5 and the pump impeller core ring 32, in order to transmit a torque from the pump impeller 3 to the inner friction disc 5 via the plurality of elastic components 7, while the plurality of elastic components 7 can absorb an abruptly changing torque.

The inner friction disc 5 serves as a component of both the lock-up clutch and the shock absorber, as described above. In this way, two components that are generally separate are combined into one, and the shock absorber, which is usually located outside the first chamber 11 formed by the impeller housing 31 and the turbine housing 41, is now located within the first chamber 11. Therefore, the hydraulic torque converter can have a smaller volume, and the space saved provides ample design options, such as the addition of further components. Furthermore, the hydraulic torque converter can be lighter, which allows for a reduction in the energy consumption of motor vehicles equipped with the torque converter, thus meeting a current environmental trend toward energy conservation and emission reduction.

Regarding the 2 , 3 until 4 The inner friction disc 5 has an outer circumferential section 52 that is located radially outside of it. The outer circumferential section 52 extends substantially radially and has a first surface 52a facing the pump impeller 3 and a second surface 52b facing the turbine 4 ( 4 How best to do this in the 1 and 4 As shown, the second surface 52b is provided with a friction plate 54 for forming a snap-fit connection with the turbine housing 41. The friction plate 54 has, for example, a ring-shaped form and is firmly attached to the second surface 52b by suitable means known in the art, such as an adhesive bond.

The turbine casing 41 has a generally annular flat flange 42. The flange 42 is a radial extension of the turbine casing 41 and is arranged radially outside the turbine blades 43a, as shown in 1 The turbine flange 42 is integrated with other parts of the turbine housing 41; for example, it may be a single or integrated component with the housing, or it may be an independent component connected to the housing. The turbine housing flange 42 overlaps axially with the second surface 52b of the inner friction disc 5. As explained below, the turbine housing 41 and its flange 42 can move axially toward or away from the second surface 52b of the inner friction disc 5 to enter the locked or unlocked position.

According to some embodiments of the present disclosure, a fluid can enter the second chamber 12 on one side of the turbine housing. Fluid flows into or out of the second chamber 12 on one side of the turbine housing 41 to drive the axial movement of the turbine housing. The fluid flow is controlled, for example, by valves. When the valve is open, the fluid can flow into the second chamber 12 on one side of the turbine housing 41, and the fluid pressure in the second chamber 12 gradually increases until it is greater than the pressure in the first chamber 11 on the other side of the turbine housing 41, thus driving the turbine housing 41 axially towards the second surface 52b of the inner friction disc 5. This engages the locking clutch. Conversely, when the valve is closed, the fluid can flow out of the second chamber 12 on one side of the turbine housing 41, so that the pressure in the second chamber 12 gradually decreases until it is less than the pressure in the first chamber 11 on the other side of the turbine housing 41. Under a pressure differential, the turbine housing 41 moves axially away from the second surface 52b of the inner friction disc 5. This disengages the lock-up clutch.

Of course, someone with technical skills can also imagine other drive methods to implement the axial movement of the turbine housing 41, such as the use of diaphragm springs.

In some embodiments of the present disclosure, with regard to 1 To limit the endpoint of the axial movement of the turbine housing 41, a first stop bushing 58 is provided on the first surface 52a of the outer circumferential section 52 of the inner friction disc 5. The first stop bushing 58 has an annular shape around the axis of rotation X for axially supporting the inner friction disc 5 when the turbine 4 is in the locked position, thereby defining the left endpoint of the movement of the turbine housing 41. Furthermore, a second stop bushing 68, also annular in shape around the axis of rotation, is arranged between the output hub 6 and the housing 2 for axially supporting the output hub 6 when the turbine 4 is in the unlocked position, thereby defining the right endpoint of the movement of the turbine housing 41.

Regarding the 2 and 6 The second stop bushing 68 is provided with a plurality of radially extending fluid passages 69 to allow the fluid to flow into and out of the second chamber 12 between the turbine housing 41 and the housing 2. The fluid inflow path is described in 8 shown schematically by arrows. However, an outflow path for the fluid can be provided.

Regarding the 1 and 4 Furthermore, a sealing ring 56 is provided on the first surface 52a of the outer circumferential section 52 of the inner friction disc 5. The sealing ring 56 has an annular shape around the axis of rotation X and is used to form a fluid seal between the impeller housing 31 and the inner friction disc 5 when the turbine 4 is in the locked position, thereby ensuring the pressure differential between the first chamber 11 and the second chamber 12. Therefore, the inner friction disc 5 and the turbine housing 41 form a tight and secure frictional connection, thus ensuring the efficiency of the torque transmission in the rigid transmission mode.

In some embodiments, with regard to 7 The first stop bushing 58 and the sealing ring 56 are connected to each other in a radial direction. For example, the first stop bushing 58 is arranged radially within the sealing ring 56 and is directly adjacent to the sealing ring 56. A plurality of centering projections 50 can be provided in the inner friction disc 5. The plurality of centering projections 50 engage an inner circumferential surface of the first stop bushing 58 to center the first stop bushing 58 with respect to the axis of rotation X, and then the sealing ring 56 is centered by radial contact with the first stop bushing 58. Optionally, the first stop bushing 58 is arranged radially outside the sealing ring 56 and is directly adjacent to the sealing ring 56. The multitude of centering projections 50 engage the inner circumferential surface of the sealing ring 56 to center the sealing ring 56 with respect to the axis of rotation X, and then the first stop bushing 58 is centered by radially butting against the sealing ring 56.

Regarding the 2 , 3 until 4 The inner friction disc 5 has an inner circumferential section 51 located on its radially inner side, which has a plurality of windows 53 for holding an elastic component. The plurality of windows 53 for holding an elastic component extend circumferentially. Two adjacent windows 53 for holding an elastic component are separated circumferentially by a radial partition 55. The plurality of elastic components 7 are held axially between the plurality of windows 53 for holding an elastic component and the pump impeller core ring 32. 5 The wheel core ring 32 has a plurality of drive strips 33 extending towards the inner friction disc 5, which also form part of the shock absorber.

In some embodiments, the elastic components 7 are as shown in 2 As shown, the inner friction disc 5 and the pump impeller core ring 32 are connected in series in the circumferential direction. Each elastic component 7 is compressed in the circumferential direction between the drive strip 33 of the pump impeller core ring 32 and the radial partition 55 of the inner friction disc 5.

In the rigid transmission mode of torque converter 1, as in 9 As shown, the inner friction disc 5 engages with the turbine housing 41. In this case, the torque input is transmitted through the housing 2 and the pump impeller 3 to the inner circumferential section 51 of the inner friction disc 5 via the drive strips 33 of the pump impeller core ring 32 and the elastic components 7 (not shown). 9 (shown) and then the outer circumferential section 52 of the inner friction disc 5 transmits the torque to the turbine housing 41 and the output hub 6 via the detent connection between the friction plate 54 and the turbine housing 41. Consequently, the fluctuation of the engine torque can be effectively absorbed and reduced in the rigid transmission mode.

In the hydraulic transmission mode (not shown) of the hydraulic torque converter 1, the inner friction disc 5 and the turbine housing 41 are disengaged. In this case, the torque input is hydraulically transmitted through the housing 2 to the turbine 4 via the pump impeller 3 and then to the output hub 6 via the turbine housing 41.

In some embodiments, as in the 3 and 4 As shown, the outer circumferential section 52 and the inner circumferential section 51 of the inner friction disc 5 are connected by a plurality of radial webs 57. A circumferentially extending fluid flow window 59 is formed between adjacent radial webs 57 to allow the fluid for hydraulic transmission, which circulates in the first chamber 11, to flow through it, while reducing the weight of the inner friction disc 5 and the entire hydraulic torque converter 1.

In relation to 3 Each radial web 57 and the corresponding radial partition 55 of the inner circumferential section 51 are aligned with each other in a radial direction, thereby improving the mechanical strength of the inner friction disc 5 as a torque transmission element.

Furthermore, regarding 1 The components of the shock absorber (the pump impeller core ring 32, the elastic components 7, and the windows 53 for holding an elastic component) are located at a central position in the radial direction of the first chamber 11, without obstructing the transmission path of the hydraulically driven fluid between the pump impeller 3 and the turbine 4. Therefore, according to the present disclosure, the hydraulic torque converter 1 fully utilizes the interior space at the radial central position of the first chamber 11 to accommodate the shock absorber, thereby significantly reducing the size of the hydraulic torque converter 1 in the radial direction and achieving a compact structure suitable for various application environments.

Various modifications, changes and variations can be implemented with the aforementioned embodiments.

The preceding description of the exemplary embodiments of the present disclosure has been set forth for illustrative purposes in accordance with the provisions of the Patent Regulations. It is not intended to be exhaustive or to limit this disclosure to the precise forms disclosed. The embodiments disclosed above have been selected to best illustrate the principles of the disclosure and its practical application, so that someone with ordinary technical skills can best utilize the disclosure in various embodiments, and various modifications are suitable for the intended specific use, provided that the principles described herein are followed.

Claims (12)

A hydraulic torque converter comprising: a housing (2) arranged around an axis of rotation (X) for receiving an input torque; a pump impeller (3) arranged around the axis of rotation (X) and comprising a pump impeller housing (31), a pump impeller core ring (32), and a plurality of pump impeller blades (34); a turbine (4) arranged around the axis of rotation (X) and axially opposite the pump impeller (3) and comprising a turbine housing (41) and a plurality of turbine blades (43); an output hub (6) arranged around the axis of rotation (X) and fixedly connected to the turbine housing (41) for outputting a torque; wherein the hydraulic torque converter further comprises an inner friction disc (5) arranged around the axis of rotation (X) and axially between the pump impeller (3) and the turbine (4). is arranged, wherein a plurality of elastic components (7) are arranged on the inner friction disc (5) and are held between the inner friction disc (5) and the pump impeller core ring (32) to transmit the torque from the pump impeller (3) to the inner friction disc (5) via the plurality of elastic components (7); and wherein the turbine (4) is displaceable between a locked position in which the turbine housing (41) engages the inner friction disc (5) and forms a latching connection with it, and a released position in which the turbine housing (41) disengages from the inner friction disc (5). Hydraulic torque converter according to Claim 1 , characterized in that the inner friction disc (5) has an annular shape and an inner circumferential section (51) located on a radially inner side thereof, and the inner circumferential section (51) has a plurality of windows (53) for holding an elastic component extending in the circumferential direction, wherein two adjacent windows (53) for holding an elastic component are separated from each other in the circumferential direction by a radial partition (55) and the plurality of elastic components are held axially between the plurality of windows (53) for holding an elastic component and the pump impeller core ring (32). Hydraulic torque converter according to Claim 2 , characterized in that the pump impeller core ring (32) has a plurality of drive strips (33) extending in the direction of the inner friction disc (5). Hydraulic torque converter according to Claim 2 or 3 , characterized in that the inner friction disc (5) has an outer circumferential section (52) located on the radially outer side of the same and has a first surface (52a) facing the pump impeller (3) and a second surface (52b) facing the turbine (4), wherein a friction plate (54) is arranged on the second surface (52b) to form a snap connection with the turbine housing (41). Hydraulic torque converter according to Claim 4 , characterized in that a first stop bushing (58) is arranged on the first surface (52a) of the outer circumferential section (52) of the inner friction disc (5), wherein the first stop bushing (58) has an annular shape around the axis of rotation (X) and is used to support the turbine (4) in the axial direction when the turbine (4) is in the locked position. Hydraulic torque converter according to Claim 5 , characterized in that a sealing ring (56) is arranged on the first surface (52a) of the outer circumferential section (52) of the inner friction disc (5). Hydraulic torque converter according to Claim 6 , characterized in that the inner friction disc (5) is provided with a plurality of centering projections (50) for centering the sealing ring (56) and/or the first stop bushing (58) relative to the axis of rotation (X). Hydraulic torque converter according to Claim 4 , characterized in that the outer circumferential section (52) and the inner circumferential section (51) of the inner friction disc (5) are connected by a plurality of radial webs (57) and circumferentially extending fluid circulation windows (59) are formed between adjacent radial webs (57). Hydraulic torque converter according to Claim 8 , characterized in that each radial web (57) and the corresponding radial partition (55) of the inner circumferential section (51) are aligned with each other in a radial direction. Hydraulic torque converter according to Claim 5 , characterized in that a second stop bushing (68) is arranged between the output hub (6) and the housing (2), wherein the second stop bushing (68) has an annular shape around the axis of rotation (X) and is used for axially supporting the output hub (6) when the turbine (4) is in the released position. Hydraulic torque converter according to Claim 7 , characterized in that the second stop bushing (68) is provided with a plurality of radially extending fluid passages (69) to allow a fluid to flow into or out of the space between the turbine housing (41) and the housing (2). Motor vehicle, characterized in that it has a hydraulic torque converter according to one of the Claims 1 until 11 exhibits.